Independent wheel suspension for a motor vehicle

ABSTRACT

Independent wheel suspensions for a motor vehicle are described herein. An example independent wheel suspension includes a link to be pivotably coupled to a vehicle body of the motor vehicle via a first flexible pivot bearing and a second flexible pivot bearing. The first and second flexible pivot bearings form a pivoting axis. The link has a wheel attachment point to which a vehicle wheel is to be coupled. The example independent wheel suspension also includes a spring to be disposed between the link and the vehicle body. The spring is configured to produce a force component on the link that is directed outward along a transverse axis of the motor vehicle and that increases during compression.

RELATED APPLICATION

This patent claims priority to German Patent Application DE102018220235.4, titled “Einzelradaufhängung für ein Kraftfahrzeug,” andfiled Nov. 26, 2018, which is hereby incorporated by reference in itsentirety.

FIELD OF THE DISCLOSURE

This disclosure relates generally to motor vehicles and, moreparticularly, to independent wheel suspensions for motor vehicles.

BACKGROUND

On modern motor vehicles, all of the wheels are connected to the body orthe chassis of the vehicle in such a way that each of the wheels canmove relative to the body. Each wheel and a wheel carrier on which thewheel is mounted are part of the unsprung mass, which, to a greater orlesser extent, follows the height of the respective driving surface,while the body and the chassis form parts of the sprung mass, whichshould be decoupled, at least to a large extent, from sudden movementsof the unsprung mass.

SUMMARY

An independent wheel suspension for a motor vehicle is disclosed herein.The independent wheel suspension includes a link to be pivotably coupledto a vehicle body of the motor vehicle via a first flexible pivotbearing and a second flexible pivot bearing. The first and secondflexible pivot bearings form a pivoting axis. The link has a wheelattachment point to which a vehicle wheel is to be coupled. Theindependent wheel suspension also includes a spring to be disposedbetween the link and the vehicle body. The is spring configured toproduce a force component on the link that is directed outward along atransverse axis of the motor vehicle and that increases duringcompression.

A motor vehicle is disclosed herein that includes a first wheel, asecond wheel, a vehicle body, and an independent wheel suspension. Theindependent wheel suspension includes a first link pivotably coupled tothe vehicle body via a first flexible pivot bearing and a secondflexible pivot bearing. The first wheel is coupled to the first link.The independent wheel suspension also includes a first spring disposedbetween the first link and the vehicle body. The first spring isconfigured to produce a first force component on the first link that isdirected outward along a transverse axis of the motor vehicle. Theindependent wheel suspension includes a second link pivotably coupled tothe vehicle body via a third flexible pivot bearing and a fourthflexible pivot bearing. The second link is pivotable independently ofthe first link. The second wheel is coupled to the second link. Theindependent wheel suspension further includes a second spring disposedbetween the second link and the vehicle body. The second spring isconfigured to produce a second force component on the second link thatis directed outward along the transverse axis of the motor vehicle.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a plan view of a first example of an independent wheelsuspension implemented on an example motor vehicle and constructed inaccordance with the teachings of this disclosure.

FIG. 2 is a front view of the example independent wheel suspension ofFIG. 1 in straight-ahead travel.

FIG. 3 is a front view of the example independent wheel suspension ofFIG. 1 when cornering.

FIG. 4 is a plan view of a second example of an independent wheelsuspension implemented on an example motor vehicle and constructed inaccordance with the teachings of this disclosure.

FIG. 5 is a front view of the example independent wheel suspension ofFIG. 4 in straight-ahead travel.

FIG. 6 is a front view of the example independent wheel suspension ofFIG. 4 when cornering.

FIG. 7 illustrates an example force vectoring spring in a relaxed state.

FIG. 8 is a plan view of a third example of an independent wheelsuspension implemented on an example motor vehicle and constructed inaccordance with the teachings of this disclosure.

The figures are not to scale. Instead, the thickness of the layers orregions may be enlarged in the drawings. In general, the same referencenumbers will be used throughout the drawing(s) and accompanying writtendescription to refer to the same or like parts. Descriptors “first,”“second,” “third,” etc. are used herein when identifying multipleelements or components which may be referred to separately. Unlessotherwise specified or understood based on their context of use, suchdescriptors are not intended to impute any meaning of priority, physicalorder or arrangement in a list, or ordering in time but are merely usedas labels for referring to multiple elements or components separatelyfor ease of understanding the disclosed examples. In some examples, thedescriptor “first” may be used to refer to an element in the detaileddescription, while the same element may be referred to in a claim with adifferent descriptor such as “second” or “third.” In such instances, itshould be understood that such descriptors are used merely for ease ofreferencing multiple elements or components.

DETAILED DESCRIPTION

In modern mobile vehicles, each of the wheels is connected to thevehicle body by one or more links in a manner that allows the links topivot about at least one axis. Depending on requirements, differentnumbers of links can be used to guide the wheel. A distinction may bedrawn between longitudinal links, diagonal links, and transverse links,depending on the path of the link relative to the vehicle or thelongitudinal axis thereof. In one known type of suspension that is usedalmost exclusively for rear axles, each wheel is pivotably connected tothe vehicle body individually by means of a single link, which is alsoreferred to as a swinging arm. The respective link can be a longitudinallink, which is therefore pivotable about a pivoting axis that isparallel to the transverse axis of the vehicle. In another instance, therespective link can be a diagonal link, in which the pivoting axis isdiagonal with respect to the transverse axis of the vehicle and withrespect to the longitudinal axis of the vehicle. The wheel carrier isusually connected in a fixed manner to the link or even manufacturedintegrally therewith. The link generally has a roughly triangularstructure, in which two pivot bearings for attachment to the vehiclebody are provided in the front region, and the wheel carrier orattachment point for the latter are provided in the rear region.

To minimize the transmission of vibration on the part of the runninggear to the vehicle body, the link is normally connected to the vehiclebody by flexible pivot bearings. Although the flexibility of thebearings suppresses the transmission of shocks and vibration in thedesired manner and thus contributes overall to ride comfort, this alsosimultaneously impairs the guidance of the link relative to the vehiclebody and thus that of the wheel. In the case of laterally acting forces,such as when cornering, the link twists relative to the vehicle bodyabout the vertical axis of the vehicle. The vehicle thus tends tooversteer, all the more so, the softer or more flexible the design ofthe bearings. In principle, this problem could be counteracted bycombining the longitudinal or diagonal links with transverse links, butthis is problematic as regards the kinematics of the axle and, in somecircumstances, may even be entirely impractical.

Disclosed herein are examples that prevent or reduce (e.g., minimize)oversteer in independent wheel suspensions that have longitudinal linksor diagonal links. Thus, the example disclosed herein counteractoversteer in the case of a vehicle axle with independent wheelsuspension. It should be noted that the features and measures presentedindividually in the following description can be combined in anytechnically feasible manner, giving rise to further examples.

Disclosed herein are example independent wheel suspensions for motorvehicles. A motor vehicle may be, for example, a passenger car or truck.The example wheel suspensions disclosed herein may be for a front wheelor a real wheel. In particular, the example wheel suspensions disclosedherein can be the wheel suspension for a driven or an undriven rearwheel. As used herein, the term “independent wheel suspension” meansthat the two wheels on an axle are suspended individually andindependently of one another and, thus, can move independently of oneanother.

An example independent wheel suspension disclosed herein has an examplelink that has example flexible pivot bearings mounted on an examplevehicle body in such a way as to be pivotable about a pivoting axis. Thepivot bearings form means for the link to be mounted in such a way as tobe pivotable relative to the vehicle body. In some examples, the link ismounted on the vehicle body in such a way as to be pivotable about apivoting axis by two flexible pivot bearings that are offset at leastrelative to the Y axis. In an XYZ reference frame, the X axiscorresponds to a longitudinal axis of the motor vehicle, the Y axiscorresponds to an axis that is transverse to the motor vehicle (e.g.,perpendicular to the longitudinal axis), and the Z axis corresponds toan axis that is perpendicular to the X and Y axes (e.g., the Z axis maybe the vertical axis). Therefore, in some examples, two pivot bearingsform the means for the link to be mounted in such a way as to bepivotable relative to the vehicle body. As used herein, “vehicle body”is used as a collective term for the body shell, the chassis, and, wherepresent, a subframe. In some examples, bearing lugs or bearing sleevesthat receive rubber-metal bushes or similar elements are formed on thelink. In some examples, a pivot pin, which is passed through therubber-metal bush, is provided on the vehicle body. In each case, bothpivot bearings are of flexible design, the primary purpose thereof beingto minimize the transmission of shocks and vibration to the vehiclebody. The arrangement of the two pivot bearings relative to one anotherdefines a pivoting axis, which normally also corresponds to thealignment of the bearing sleeves or similar elements. In some examples,the two pivot bearings are arranged offset with respect to one anotherin relation to the Y axis, and therefore the pivoting axis is at anangle, i.e. not parallel, to the X axis. In some examples, the pivotbearings can additionally also be arranged offset with respect to oneanother in relation to the X axis and/or in relation to the Z axis.

The example link has an example wheel attachment point for direct orindirect attachment of a vehicle wheel. The wheel attachment point canbe used to secure a wheel carrier. In other examples, the wheel carrieris formed on the link itself. A wheel carrier or knuckle of this kind isprovided for the purpose of mounting the wheel, which is thus rotatablymounted relative thereto in the installed state. The two pivot bearingsand the wheel attachment point form a substantially triangulararrangement. In some examples, the link can also be referred to as anA-arm. The link can be constructed of any material and other linkconfigurations are possible. For example, the link can be manufacturedas a shell structure including sheet metal parts, the link can bemanufactured from gray cast iron or light metal (e.g., aluminum), thelink can be manufactured from composite material or fiber-reinforcedplastic, or a combination of the aforementioned materials. The link canhave a more or less sheet-like form or can have several arms, on theends of which the pivot bearings or wheel attachment point,respectively, are arranged. Arms of this kind can be of straight, curvedand/or angled design.

In some examples, the link is coupled, directly or indirectly, to thevehicle body by means of an example spring unit or element. As such, thevehicle body is supported, directly or indirectly, on the link via thespring unit. In such an example, the spring element unit provides springsupport for the wheel relative to the vehicle body. The spring unit canbe mounted either directly on the link or, alternatively, on a componentconnected thereto (e.g., a wheel carrier) if the latter is not formedintegrally with the link. The spring unit is used to decouple thevehicle body (i.e., the sprung mass of the vehicle) from the unsprungmass. In the case of a vertical deflection of the wheel and thus of thelink relative to the vehicle body, there is an elastic deformation ofthe spring unit, which leads in turn to a restoring force. The springunit can be of single-part or multi-part design. In some examples, thespring unit is passive (i.e., it does not have any actuators or a motordrive).

In some examples, the link can be connected directly or indirectly tothe vehicle body via a damper (e.g., as part of a shock absorber). Thedamper dampens oscillations by converting kinetic energy into heat. Thedamper can be combined spatially with the spring unit.

In examples disclosed herein, the spring unit is configured or designedto produce a force component on the link that is directed outward alongthe Y axis (a transverse axis of the motor vehicle) and increases duringcompression. The spring unit is therefore configured or designed toproduce a force component on the link that is directed outward along theY axis. As disclosed above, the spring unit can transmit the forcecomponent to the link directly or indirectly (e.g., via at least oneinterposed component). The corresponding force component acts along theY axis, i.e., in the transverse direction, outward from the vehiclecenter or vehicle center plane. If compression occurs because ofincreasing static or dynamic loading (i.e., a vertical deflection of avehicle wheel relative to the vehicle body), the corresponding forcecomponent increases. In the absence of compression (e.g., at normalload), the corresponding force component is zero and, thus, increasesduring compression, starting from zero.

During cornering, compression occurs at the wheel on the outside of thebend. At the same time, the inertia of the vehicle body leads to atendency for the vehicle body to be pushed outward in relation to thebend, relative to the link and the wheel arranged thereon. As viewedfrom the vehicle body, the wheel on the outside of the bend or the linkon the outside of the bend is subject to a force acting toward thecenter of the vehicle or a corresponding torque around the verticalaxis. In known designs, this force would result in oversteer. However,in examples disclosed herein, this force is counteracted by the forcecomponent produced by the spring unit. Depending on the example or theinstantaneous loading, the oversteer can be completely or partiallysuppressed. The example wheel suspension or spring unit are designed orset up in such a way that, when the vehicle is traveling straight ahead,alignment of the wheel parallel to the direction of travel results fromthe sum total of the forces acting laterally (i.e., along the Y axis) oneach of the wheels or each of the links. Therefore, if the spring unitproduces a lateral force component even in straight-ahead travel, thelateral force component can be compensated by bearing forces at thewheel attachment points, for example.

In some examples disclosed herein, it is advantageous that oversteer iscounteracted by a purely passive spring unit. In other words, no activeelements that would complicate the structure of the wheel suspension arerequired. The spring unit also takes at least some part in the usualfunction of a spring support for the link or the wheel arranged thereonrelative to the vehicle body. In some examples disclosed herein, thereis no need for any additional components to a standard motor vehicle,but only for modification or arrangement of components that are alreadypresent.

In some examples, the spring unit is advantageously configured in such away that the outwardly directed force component increases monotonicallyas a function of a wheel load of the vehicle wheel. In other words, thegreater the wheel load, the greater is the outward-directed forcecomponent. In this case, the outward-directed force component duringrebound is reduced. This ensures that oversteer is likewise counteractedat the wheel on the inside of the bend, which usually rebounds. Duringcornering, the inertia of the vehicle body normally imposes on thiswheel on the inside of the bend a force or torque that pushes the wheeloutward relative to the vehicle body (i.e., away from the vehiclecenter). This likewise corresponds to oversteer. By virtue of the factthat the outward-directed force component produced by the spring unit isreduced as compared with straight-ahead travel, the oversteer at thewheel on the inside of the bend is also at least reduced or evenprevented.

In some examples disclosed herein, the pivoting axis of the link isparallel to the Y axis (the transverse axis of the motor vehicle),wherein the link is designed as a longitudinal link. In other words, thetwo pivot bearings are at the same position in relation to the X axisand the Z axis and are offset with respect to one another, normallyspaced apart, only along the Y axis. The link is designed as alongitudinal link and extends rearward from the pivot bearings, relativeto the X axis. Normally, the wheel attachment point corresponds to therearmost part of the link. The advantages of the example wheelsuspensions disclosed herein are more impactful with this type oflongitudinal link because the lateral forces (i.e., the forces acting inthe direction of the Y axis) act on the link with a large effectivelever arm. The at least partial compensation of such forces is thereforeparticularly important when cornering in order to stabilize the track ofthe respective wheel.

In other examples disclosed herein, the pivoting axis is at an anglerelative to the Y axis (the transverse axis of the motor vehicle),wherein the link is designed as a diagonal link, sometimes referred as asemi-trailing axle. The pivoting axes of the links arranged on the twosides are symmetrical with respect to the vehicle center plane. Thepivoting axes each extend diagonally with respect to the X-Y plane, i.e.neither parallel to the X axis nor parallel to the Y axis. The pivotingaxis can be at any angle relative to the Y axis. In some examples, thepivoting axis is between 10° and 45° relative to the Y axis. Thepivoting axis can additionally be at an angle to the X-Y plane, i.e. thetwo pivot bearings can additionally be offset with respect to oneanother in relation to the Z axis, i.e. they can have a vertical offset.In other words, the projection of the respective pivoting axis on theX-Y plane is at an angle to the X axis and to the Y axis.

In some examples disclosed herein, the spring unit includes a spring.The spring has a line of action that slopes inward toward the Y axisrelative to the Z axis. As such, the line of action of force correspondsto the effective path of the force produced by the spring. If the lineof action of force slopes inward toward the Y axis relative to the Zaxis, i.e., the line of action of force extends inward (i.e., toward thevehicle center) when viewed from the bottom up, the spring produces avertical force component that serves to support the vehicle body, and ahorizontal force component, namely the outward-directed force component.Both force components increase during compression. Depending onrequirements, the magnitude of the selected slope of the line of actionof force relative to the Z axis can differ. In some examples, themagnitude of the slope is below 45°, such that the vertical forcecomponent is larger than the outward-directed force component.

The spring can be supported on a wheel carrier manufactured separatelyfrom the link, for example. In some examples, it is advantageous thatthe spring is supported on the link. The spring may be supported on anupper side of the link, such as via a spring plate or some othersuitable element, by means of which a secure connection between thespring and the link is achieved. In some examples, the spring is mountedin an articulated manner on the link, thus allowing a certain pivotingmovement.

The slope of the line of action of force disclosed herein is achieved invarious manners. In one example, the spring is disposed such that acenter line of the spring is sloped inward toward the Y axis relative tothe Z axis. In the case of a cylindrical coil spring, the center line orspring center line corresponds to the cylinder axis. In the case ofnon-cylindrical springs, such as those in which the individual turnsthat have different diameters and/or are offset with respect to oneanother, for example, a type of central point of each individual turn isnormally constructed and the central points are connected by animaginary line, which then forms the center line. However, the examplesdisclosed herein are not limited to coil springs. Instead, other typesof spring (e.g., pneumatic springs) can also be employed.

Additionally or alternatively, the line of action of force of the springslopes inward toward the Y axis relative to the center line of thespring. In other words, the line of action of force is tilted or slopesin the Y-Z plane relative to the center line. The projection of the lineof action of force onto the Y-Z plane is at an angle to the projectionof the center line. Mathematically, this can also be interpreted as arotation around the X axis. In this example, the slope of the line ofaction of force is not achieved (or at least not exclusively achieved)by a slope of the spring but by the design of the spring. Springs ofthis kind are also referred to as force vectoring springs. While thecenter line thereof may be curved in the unloaded state, springs of thiskind are normally designed in such a way that they can also produce astraight center line under normal load in the installed state. In thisstate, the external dimensions can correspond at least substantially toa conventional spring, in which the line of action of force coincideswith the center line. A force vectoring spring of this kind can beinstalled in such a way that the center line thereof is parallel to theZ axis (i.e., a slope of the spring overall is unnecessary). In someexamples, this is advantageous for the overall size of the wheelsuspension. Often, there are limits to the installation of a slopingspring for design reasons, and these limits therefore also exist inrespect of the influencing of the outward-directed force component. Withthe differing line of action of force described, these limits can beovercome. Therefore, the examples disclosed herein can produce anoutward-directed force component and also adapt to different variants ofa vehicle model without changing the installation position ordimensioning of the spring. For this purpose, all that would be requiredwould be to use a spring with a different line of action of force.

The example spring can be implemented in different forms ofconstruction, such as a pneumatic spring. In some examples, the springis designed as a coil spring. Some such coil springs include springsteel or fiber composite plastic. A coil spring in which the line ofaction of force and the center line coincide is normally straight andcylindrical in the relaxed state. In other examples, other designs maybe used, such as a coil spring in which the radius of curvature of theindividual turns varies, for example, or, alternatively, the center lineis curved in the relaxed state.

In some examples disclosed herein, the spring is S-shaped in the relaxedstate. This refers to the shape of the spring or of the center linethereof in the relaxed state. Springs of this kind are normally straightin the extended or compressed state. However, in the extended state thespring has a line of action of force that does not coincide with thecenter line but is at an angle to said line. A similar effect can alsobe achieved with pneumatic springs having a rolling bellows composed ofa fiber-rubber composite. In this case, a line of action of force at anangle to the geometric center line of the pneumatic spring is achievedthrough the asymmetric configuration of the rolling bellows.

Now turning to the figures, FIG. 1 illustrates an example independentwheel suspension 1 implemented on an example motor vehicle 100 (e.g., acar). The plane of the drawing in FIG. 1 corresponds to the X-Y plane ofthe motor vehicle 100. The motor vehicle 100 includes first and secondwheels 5, 15 that are each connected to a vehicle body 20 by respectivefirst and second links 2, 12. In this example, the first and secondwheels 5, 15 are rear wheels. However, in other examples, the exampleindependent wheel suspension 1 can similarly be implemented inconnection with front wheels. In the illustrated example, the first link2 has first and second pivot bearings 2.1 in a front region that definea first pivoting axis S₁. Similarly, the second link 12 has third andfourth pivot bearings 12.1 in a front region that define a secondpivoting axis S₂. Each of the pivot bearings 2.1, 12.1 is a flexiblebearing (e.g., constructed by a rubber-metal bush), which is mounted ina bearing sleeve formed on the link 2, 12. The two pivot bearings 2.1,12.1 of each of the links 2, 12 are offset with respect to one another,parallel to the Y axis, as a result of which the respective pivotingaxis S₁, S₂ is also parallel to the Y axis.

Each of the wheels 5, 15 is guided by means of a wheel carrier, which,in this example, is formed integrally with the respective links 2, 12 atrespective first and second wheel attachment points 2.2, 12.2. Each ofthe links 2, 12 is provided with spring support relative to the vehiclebody 20 by respective first and second passive spring units 3, 13. Inthis example, the first spring unit 3 is formed by a first spring 4, andthe second spring unit 13 is formed by a second spring 14. The firstspring 4 is disposed between the first link 2 and the vehicle body 20,and the second spring 14 is disposed between the second link 12 and thevehicle body 20. In this examples, the first and second springs 4, 14are coil springs. As can be seen particularly in the front view of FIG.2, the first and second springs 4, 14 are not parallel to the Z axis.Instead, a first center line M₁ of the first spring 4 slopes inwardtoward the Y axis, i.e. toward the vehicle center. Similarly, a secondcenter line M₂ of the second spring 14 slopes inward toward the Y axis,i.e. toward the vehicle center. In this example, each of the springs 4,14 is a conventional, uniform coil spring. A first line of action offorce W₁ of the first spring 4 coincides with (i.e., is aligned with)the first center line M₁ and likewise slopes relative to the Z axis.Similarly, a second line of action of force W₂ of the second spring 14coincides with (i.e., is aligned with) the second center line M₂ andlikewise slopes relative to the Z axis.

FIG. 2 corresponds to a state of the motor vehicle 100 under normal loadand in straight-ahead travel. Both of the springs 4, 14 are subject tothe same loads. FIG. 3 is a front view corresponding to FIG. 2 but inwhich the motor vehicle 100 is cornering. As a result, the second wheel15 on the outside of the bend is subject to higher loads than the firstwheel 5 on the inside of the bend. In corresponding fashion, a largervertical force component F_(2z) acts within the second spring 14 on theoutside of the bend than in the first spring 4 on the inside of thebend. Because the spring force acts parallel to the respective line ofaction of force W₁, W₂ and, thus, to the center line M₁, M₂, the slopeof the springs 4, 14 results in a smaller first vertical force componentF_(1z) in the first spring 4 on the inside of the bend. Further, a firstforce component F_(1y) directed outward parallel to the Y axis issmaller in the case of the first spring 4 on the inside of the bend thanthe corresponding second force component F_(2y) in the second spring 14on the outside of the bend.

The larger outward-directed second force component F_(2y) in the secondspring 14 on the outside of the bend produces a torque on the secondlink 12 that tends to turn the second link 12 outward, as it were out ofthe bend. Therefore, the second spring 14 is configured to produce aforce component on the second link 12 that is directed outward along atransverse axis (the Y axis) of the motor vehicle 100 and that increasesduring compression. The outward-directed second force component F_(2y)therefore compensates fully or partially for an opposite force componentthat results from the inertia of the vehicle body 20 and from thefriction of the second wheel 15 on the driving surface during cornering.Thus, oversteer is at least partially reduced or prevented.

Likewise, the first spring 4 on the inside of the bend is relaxed incomparison with straight-ahead travel, with the result that there theoutward-directed first force component F_(1y) decreases in comparisonwith straight-ahead travel. Because of other forces produced in thefirst and second pivot bearings 2.1, the first link 2 on the inside ofthe bend is also subject to a torque that counteracts oversteer.However, if the motor vehicle 100 were to turn in the other direction,the outward-directed first force component F_(1y) would increase tocounteract oversteer. Therefore, the first spring 14 is also configuredto produce a force component on the first link 2 that is directedoutward along a transverse axis (the Y axis) of the motor vehicle 100and that increases during compression. With the construction shown, itis thus possible at least to limit, or prevent, oversteer, even if thepivot bearings 2.1, 12.1 have a relatively high flexibility, in order toenhance ride comfort for instance

In some examples, each of the links 2, 12 is connected to the vehiclebody 20 by a shock damper. In the illustrated example, the two links 2,12 are not connected by a stabilizer, transverse link, or twist beam.However, in other examples, the two links 2, 12 can be connected to oneanother by a stabilizer, by means of which rolling movements of thevehicle body 20 are limited. In such an example, the stabilizer would benon-rigidly coupled to the links 2, 12.

FIGS. 4-6 illustrate a second example of an independent wheel suspension1 implemented in connection with a motor vehicle 100. The views andparts shown in FIGS. 4-6 correspond largely to the first example shownin FIGS. 1-3 and to this extent are not explained again. In thisexample, however, use is made of coil springs 4, 14, with which thelines of action of force W₁, W₂ slopes inward toward the Y axis relativeto the center lines M₁, M₂. However, the respective springs 4, 14 andthe respective center lines M₁, M₂ thereof are aligned vertically, i.e.parallel to the Z axis. In this example, the lines of action of forceW₁, W₂, which deviate from the center lines M₁, M₂, are achieved throughthe respective springs 4, 14 being S-shaped in the relaxed state. FIG. 7illustrates the first spring 4, which, in this example, is S-shaped inthe relaxed state. In the installed state, in which the springs 4, 14are aligned in a straight line, an asymmetric force distribution isthereby obtained within the springs 4, 14, leading to the illustratedslope of the lines of action of force W₁, W₂. As can be seen from acomparison of FIG. 6, which once again illustrates cornering, with FIG.3, an outward-directed force component F_(1y), F_(2y), which is smallerat the first wheel 5 on the inside of the bend than at the second wheel15 on the outside of the bend, is produced in this example too.Therefore, oversteer can at least be reduced or prevented. In theexample shown in FIGS. 4-6, it is advantageous that it is not necessaryto set the springs 4, 14 at an oblique angle, and therefore the springs4, 14 can be integrated much more easily into the overall wheelsuspension 1. It is possible to produce or vary the outward-directedforce component F_(1y), F_(2y) without having to adapt the externaldimensions or installation position of the spring 4, 14.

FIG. 8 shows, in a plan view corresponding to FIG. 1 and FIG. 4, a thirdexample of a wheel suspension 1 implemented in connection with a motorvehicle 100. The example of FIG. 8 is largely the same as the exampleshown in FIGS. 4-6, which includes use of s-shaped springs 4, 14.However, in this example, the links 2, 12 are designed as diagonallinks. As such, the pivot bearings 2.1, 12.1 of the respective links 2,12 are arranged offset with respect to one another not only in the Ydirection but also in the X direction. Thus, the respective pivotingaxes S₁, S₂ extends diagonally within the X-Y plane. In the exampleshown in FIG. 8, as in FIGS. 4-6, the springs 4, 14 are alignedvertically, but the lines of action of force W₁, W₂ slope inwardrelative to the center lines M₁, M₂. Alternatively, conventional coilsprings (such as used in the example of FIGS. 1-3) that are slopedinward could be used.

Example apparatus, systems, and articles for reducing or preventingoversteer are disclosed herein. Further examples and combinationsthereof include the following:

Example 1 an independent wheel suspension for a motor vehicle. Theindependent wheel suspension includes a link to be pivotably coupled toa vehicle body of the motor vehicle via a first flexible pivot bearingand a second flexible pivot bearing. The first and second flexible pivotbearings form a pivoting axis. The link has a wheel attachment point towhich a vehicle wheel is to be coupled. The independent wheel suspensionalso includes a spring to be disposed between the link and the vehiclebody. The spring is configured to produce a force component on the linkthat is directed outward along a transverse axis of the motor vehicleand that increases during compression.

Example 2 includes the independent wheel suspension of Example 1,wherein the spring is configured in such a way that the force componentincreases monotonically as a function of a wheel load of the vehiclewheel.

Example 3 includes the independent wheel suspension of Examples 1 or 2,wherein the pivoting axis is parallel to the transverse axis.

Example 4 includes the independent wheel suspension of Examples 1 or 2,wherein the pivoting axis is at an angle relative to the transverseaxis.

Example 5 includes the independent wheel suspension of any of Examples1-4, wherein a line of action of force of the spring slopes inwardtoward the transverse axis relative to a vertical axis.

Example 6 includes the independent wheel suspension of Example 5,wherein a center line of the spring is aligned with the line of actionof force and slopes inward toward the transverse axis relative to thevertical axis.

Example 7 includes the independent wheel suspension of Example 5,wherein the spring is S-shaped in a relaxed state.

Example 8 includes the independent wheel suspension of Example 7,wherein the line of action of force of the spring slopes inward towardthe transverse axis relative to a center line of the spring.

Example 9 includes the independent wheel suspension of any of claims1-8, wherein the spring is a coil spring.

Example 10 includes the independent wheel suspension of any of Examples1-9, wherein the spring is supported on the link.

Example 11 includes the independent wheel suspension of any of Examples1-10, wherein the spring passive.

Example 12 includes a motor vehicle including a first wheel, a secondwheel, a vehicle body, and an independent wheel suspension. Theindependent wheel suspension includes a first link pivotably coupled tothe vehicle body via a first flexible pivot bearing and a secondflexible pivot bearing. The first wheel is coupled to the first link.The independent wheel suspension also includes a first spring disposedbetween the first link and the vehicle body. The first spring isconfigured to produce a first force component on the first link that isdirected outward along a transverse axis of the motor vehicle. Theindependent wheel suspension includes a second link pivotably coupled tothe vehicle body via a third flexible pivot bearing and a fourthflexible pivot bearing. The second link is pivotable independently ofthe first link. The second wheel is coupled to the second link. Theindependent wheel suspension further includes a second spring disposedbetween the second link and the vehicle body. The second spring isconfigured to produce a second force component on the second link thatis directed outward along the transverse axis of the motor vehicle.

Example 13 includes the motor vehicle of Example 12, wherein the firstand second flexible pivot bearings form a first pivoting axis and thethird and fourth flexible pivot bearings form a second pivoting axisthat is aligned with the first pivoting axis.

Example 14 includes the motor vehicle of Example 13, wherein the firstand second pivoting axes are parallel to the transverse axis of themotor vehicle.

Example 15 includes the motor vehicle of Example 12, wherein the firstand second flexible pivot bearings form a first pivoting axis that is anangle relative to the transverse axis, and the third and fourth flexiblepivot bearings form a second pivoting axis that is at an angle relativeto the transverse axis.

Example 16 includes the motor vehicle of any of Examples 12-15, whereina first line of action of force of the first spring and a second line ofaction of force of the second spring slope inward toward the transverseaxis relative to a vertical axis.

Example 17 includes the motor vehicle of Example 16, wherein a firstcenter line of the first spring is aligned with the first line of actionof force, and the second center line of the second spring is alignedwith the second line of action of force.

Example 18 includes the motor vehicle of Example 16, wherein the firstspring is S-shaped in a relaxed state and the second spring is S-shapedin a relaxed state.

Example 19 includes the motor vehicle of Example 16, wherein the firstline of action of force of the first spring slopes inward toward thetransverse axis relative to a first center line of the first spring, andwherein the second line of action of force of the second spring slopesinward toward the transverse axis relative to a second center line ofthe second spring.

Example 20 includes the motor vehicle of any of Examples 12-19, whereinthe first and second links are not connected by a twist beam.

Example 21 includes an independent wheel suspension for a motor vehicle.The example independent wheel suspension has a link that has flexiblepivot bearings that are mounted on a vehicle body in such a way as to bepivotable about a pivoting axis, which has a wheel attachment point forthe at least indirect attachment of a vehicle wheel and which isconnected at least indirectly to the vehicle body by means of a passivespring unit. The spring unit is designed to produce a force component onthe link that is directed outward along the Y axis and increases duringcompression.

Example 22 includes the independent wheel suspension of Example 21,wherein the spring unit is configured in such a way that the outwardlydirected force component increases monotonically as a function of awheel load of the vehicle wheel.

Example 23 includes the independent wheel suspension of Example 21 or22, wherein the pivoting axis is parallel to the Y axis, and wherein thelink is designed as a longitudinal link.

Example 24 includes the independent wheel suspension of Example 21 or22, wherein the pivoting axis is at an angle to the Y axis, wherein thelink is designed as a diagonal link.

Example 25 includes the independent wheel suspension of any of Examples21-24, wherein the spring unit has a spring, the line of action of forceof which slopes inward toward the Y axis relative to the Z axis.

Example 26 includes the independent wheel suspension of any of Examples21-25, wherein the spring is supported on the link.

Example 27 includes the independent wheel suspension of any of Examples21-26, wherein a center line of the spring slopes inward toward the Yaxis relative to the Z axis.

Example 28 includes the independent wheel suspension of any of Examples21-27, wherein the line of action of force of the spring slopes inwardtoward the Y axis relative to the center line of the spring.

Example 29 includes the independent wheel suspension of any of Examples21-28, wherein the spring is designed as a coil spring.

Example 30 includes the independent wheel suspension of any of Examples21-29, wherein the spring is S-shaped in the relaxed state.

Although certain example methods, apparatus and articles of manufacturehave been disclosed herein, the scope of coverage of this patent is notlimited thereto. On the contrary, this patent covers all methods,apparatus and articles of manufacture fairly falling within the scope ofthe claims of this patent.

The following claims are hereby incorporated into this DetailedDescription by this reference, with each claim standing on its own as aseparate embodiment of the present disclosure.

What is claimed is:
 1. An independent wheel suspension for a motorvehicle, the independent wheel suspension comprising: a link to bepivotably coupled to a vehicle body of the motor vehicle via a firstflexible pivot bearing and a second flexible pivot bearing, the firstand second flexible pivot bearings forming a pivoting axis, the linkhaving a wheel attachment point to which a vehicle wheel is to becoupled; and a spring to be disposed between the link and the vehiclebody, the spring configured to produce a force component on the linkthat is directed outward along a transverse axis of the motor vehicleand that increases during compression.
 2. The independent wheelsuspension of claim 1, wherein the spring is configured in such a waythat the force component increases monotonically as a function of awheel load of the vehicle wheel.
 3. The independent wheel suspension ofclaim 1, wherein the pivoting axis is parallel to the transverse axis.4. The independent wheel suspension of claim 1, wherein the pivotingaxis is at an angle relative to the transverse axis.
 5. The independentwheel suspension of claim 1, wherein a line of action of force of thespring slopes inward toward the transverse axis relative to a verticalaxis.
 6. The independent wheel suspension of claim 5, wherein a centerline of the spring is aligned with the line of action of force andslopes inward toward the transverse axis relative to the vertical axis.7. The independent wheel suspension of claim 5, wherein the spring isS-shaped in a relaxed state.
 8. The independent wheel suspension ofclaim 7, wherein the line of action of force of the spring slopes inwardtoward the transverse axis relative to a center line of the spring. 9.The independent wheel suspension of claim 8, wherein the spring is acoil spring.
 10. The independent wheel suspension of claim 1, whereinthe spring is supported on the link.
 11. The independent wheelsuspension of claim 1, wherein the spring passive.
 12. A motor vehiclecomprising: a first wheel; a second wheel a vehicle body; and anindependent wheel suspension including: a first link pivotably coupledto the vehicle body via a first flexible pivot bearing and a secondflexible pivot bearing, the first wheel coupled to the first link; afirst spring disposed between the first link and the vehicle body, thefirst spring configured to produce a first force component on the firstlink that is directed outward along a transverse axis of the motorvehicle; a second link pivotably coupled to the vehicle body via a thirdflexible pivot bearing and a fourth flexible pivot bearing, the secondlink pivotable independently of the first link, the second wheel coupledto the second link; and a second spring disposed between the second linkand the vehicle body, the second spring configured to produce a secondforce component on the second link that is directed outward along thetransverse axis of the motor vehicle.
 13. The motor vehicle of claim 12,wherein the first and second flexible pivot bearings form a firstpivoting axis and the third and fourth flexible pivot bearings form asecond pivoting axis that is aligned with the first pivoting axis. 14.The motor vehicle of claim 13, wherein the first and second pivotingaxes are parallel to the transverse axis of the motor vehicle.
 15. Themotor vehicle of claim 12, wherein the first and second flexible pivotbearings form a first pivoting axis that is an angle relative to thetransverse axis, and the third and fourth flexible pivot bearings form asecond pivoting axis that is at an angle relative to the transverseaxis.
 16. The motor vehicle of claim 12, wherein a first line of actionof force of the first spring and a second line of action of force of thesecond spring slope inward toward the transverse axis relative to avertical axis.
 17. The motor vehicle of claim 16, wherein a first centerline of the first spring is aligned with the first line of action offorce, and the second center line of the second spring is aligned withthe second line of action of force.
 18. The motor vehicle of claim 16,wherein the first spring is S-shaped in a relaxed state and the secondspring is S-shaped in a relaxed state.
 19. The motor vehicle of claim16, wherein the first line of action of force of the first spring slopesinward toward the transverse axis relative to a first center line of thefirst spring, and wherein the second line of action of force of thesecond spring slopes inward toward the transverse axis relative to asecond center line of the second spring.
 20. The motor vehicle of claim12, wherein the first and second links are not connected by a twistbeam.